JP2886850B1 - Flow path switching device for refrigerant gas in air conditioner - Google Patents

Abstract

Kind Code: A1 Abstract: A sealing material is pressed and moved by a pressure difference between a high-pressure inlet and a high-pressure outlet without a special device or mechanism for pressing a switching rotor against a valve seat. The present invention provides a rotary type flow path switching device that has a simple structure and high reliability by performing pressure bonding to ensure an airtight state between a high-pressure outlet and a heat exchanger connection port. A switching rotor (4) built in a housing (1).
In the refrigerant gas flow path switching device in the cooling and heating device in which the flow path of the high pressure refrigerant gas is switched by turning in one direction or the other direction, the effective pressure receiving area S1 of the high pressure inlet 14 in the switching rotor and the effective pressure receiving area S1 The effective pressure receiving area S2 of the high-pressure outlet is set in a relationship of S2 <S1, and S2 and S1
The switching rotor 4 is pressed by the differential pressure of the applied pressure based on the pressure receiving area difference, and the sealing materials 19 and 20 interposed between the high pressure outlets 15 and 16 and the heat exchanger connection ports 12 and 13 are pressed and the airtight state is established. Form.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a refrigerant gas flow switching device in a cooling and heating apparatus for selectively supplying high-pressure refrigerant gas discharged from a compressor to one end and the other end of a heat exchanger.

[0002]

2. Description of the Related Art As an example, in Japanese Patent Application Laid-Open No. 8-327183, a switching rotor is built in a housing, and the housing is connected to a compressor connection port for connecting to a high pressure outlet of a compressor and to one end and the other end of a heat exchanger. Two heat exchanger ports are provided, while the switching rotor is provided with a high-pressure inlet port communicating with the compressor port and a high-pressure outlet port selectively communicating with one of the heat exchanger ports. By rotating the switching rotor in one direction or the other direction on the valve seat surface integral with the housing, the two high-pressure outlets opened on the sliding contact surface are opened on the sliding contact surface. Disclosed is a refrigerant gas flow path switching device in a cooling and heating device that can selectively switch communication with an exchanger connection port.

[0003]

In the switching device, a sealing material is provided at the high-pressure outlet so as to be in close contact with the valve seat surface, so that the high-pressure outlet and each of the heat exchanger connection ports are air-tight. However, it is difficult to secure airtightness by merely interposing a sealing material, and there is a problem that high-pressure refrigerant gas leaks into the housing and switching between cooling and heating is not properly guaranteed.

[0004] The airtight defect is also caused by the inclination of the switching rotor, the surface accuracy of the valve seat, and the like.

[0005]

SUMMARY OF THE INVENTION The present invention secures the airtightness between the high-pressure outlet and the heat exchanger connection port on the sliding rotation surface of the switching rotor and the valve seat, and aims at switching between cooling and heating by the switching rotor. It has been achieved appropriately.

In short, the present invention provides a cooling and heating system in which selective communication between the high-pressure outlet and the two heat exchanger ports is achieved by rotating the switching rotor in one direction or the other at a fixed angle. In the apparatus for switching the flow path of the refrigerant gas in the apparatus, an effective pressure receiving area S1 for the high-pressure refrigerant gas at the high-pressure inlet is provided.
And the effective pressure receiving area S2 of the high-pressure outlet with respect to the high-pressure refrigerant gas is set in a relationship of S2 <S1, and the switching rotor is moved in the direction of the heat exchanger connection port by a differential pressure of the applied pressure based on the pressure receiving area difference between S2 and S1. The sealing material interposed between the high-pressure outlet and the heat exchanger connection port is pressed against the periphery of the high-pressure outlet and / or the heat exchanger connection port to form an airtight state.

According to an embodiment of the present invention, the sealing material is disposed between the high-pressure outlet of the switching rotor and the heat exchanger connection port by a small amount in a crimping direction and a direction opposite thereto in a non-crimping manner. The switching rotor is moved in the direction of the rotation axis by the differential pressure of the applied pressure based on the area difference, and both end faces of the sealing material are pressed against the peripheral edge of the high-pressure outlet and the peripheral edge of the heat exchanger connection port of the switching rotor. Configure as shown.

Further, according to the embodiment, a supplementary pressure spring for elastically pressing the switching rotor toward the heat exchanger connection port side is provided so that a more reliable airtight state can be achieved in cooperation with the differential pressure.

Further, the rotating shaft of the switching rotor penetrates through the housing and protrudes to the outside, and the rotor is pressed against the sealing material disposed on the inner peripheral edge of the through-hole by the pressure difference of the applied pressure, so that the rotating shaft has a through-hole. A configuration for airtightness can be used together.

[0010]

DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiments of the present invention will be described below with reference to FIGS.

As shown in FIGS. 1 to 4, the opening surface of the cup-shaped cover 2 is hermetically closed by a valve seat 3 made of a flat plate to form a housing 1 having a low-pressure chamber 7.

The cup-shaped cover 2 is formed in a circular shape by subjecting a metal plate to a drawing press process, and the valve seat 3 is punched out of a circular shape from the metal plate, and is fitted into an opening of the cup-shaped cover 2. At the fitting portion, airtightness is achieved by welding or the like in an annular shape, and the two and the two are integrated.

On the other hand, similarly to the housing 1, the opening surface of the cup-shaped cover 5 is hermetically closed by a valve seat 6 made of a flat plate to form a switching rotor 4 having a high-pressure chamber 8.

The cup-shaped cover 5 is formed into a substantially square box shape by subjecting a metal plate to drawing press processing, and the valve seat 6 is punched into a substantially square shape from the metal plate. At the same time, airtightness is achieved by annularly welding or the like at this fitting portion, and the two 5 and 6 are integrated.

The switching rotor 4 is housed in the low-pressure chamber 7 of the housing 1.

The housing 1 is provided with a compressor connection port 10 connected to the high pressure outlet of the compressor 9 and first and second heat exchanger connection ports 12 and 13 connected to one end and the other end of the heat exchanger 11.

On the other hand, the switching rotor 4 has a high-pressure inlet 14 constantly communicating with the compressor connection port 10 and first and second high-pressure introduction ports selectively communicating with one of the heat exchanger connection ports 12 and 13. Exits 15 and 16 are provided.

The switching rotor 4 has a rotation axis z passing through the center of the housing 1 at the center thereof. Therefore, this rotation axis z passes through the centers of the cup-shaped covers 5, 2 and the valve seats 6, 3.

The compressor connection port 10 is opened around the center of the cup-shaped cover 2, that is, the rotation axis z, and similarly, the high-pressure inlet 14 is opened around the center of the cup-shaped cover 5, that is, the rotation axis z. And both 10,14
Are concentrically connected about the rotation axis z.

On the other hand, the first and second heat exchanger connection ports 12,
13 is provided on the valve seat 3, and both connection ports 12, 13 are connected to the rotation axis z.
Are arranged at an equal distance from each other with a constant angle of opening.
The second high-pressure outlets 15 and 16 are provided in the valve seat 6, and the two high-pressure outlets 15 and 16 are disposed equidistantly from the rotation axis z with a constant opening angle.

For example, the first heat exchanger connection port 12 and the second
The heat exchanger connection port 13 is arranged with an opening angle smaller than 180 degrees, and the first high-pressure outlet 15 and the second high-pressure outlet 16 are arranged.
Is arranged with an opening angle of 180 degrees. The switching rotor 4 has a symmetrical shape about the axis z, and has the first high-pressure outlet 15 at one end and the second high-pressure outlet 1 at the other end.
6 are arranged symmetrically and balanced with respect to high pressure.

The high-pressure inlet 14 and the first and second high-pressure outlets 15 and 16 communicate with each other via a high-pressure chamber 8. The high-pressure refrigerant gas introduced through the compressor connection port 10 and the high-pressure inlet 14 is supplied to the high-pressure chamber. 8 and is supplied to the first high-pressure outlet 15 or the second high-pressure outlet 16.

As shown in FIG. 1, when the switching rotor 4 rotates in one direction at a predetermined angle about the rotation axis z, the first high-pressure outlet 15 and the first heat exchanger connection port 12 communicate with each other. The high-pressure refrigerant gas filling the high-pressure chamber 8 is supplied to one end of the heat exchanger 11 through the first high-pressure outlet 15 and the first heat exchanger connection port 12.

The rotation of the switching rotor 4 causes the second high-pressure outlet 16 to slide and rotate on the valve seat surface to open the second heat exchanger connection port 13. The low-pressure refrigerant gas to be led out is introduced into the low-pressure chamber 7 through the open second heat exchanger connection port 13, and the low-pressure refrigerant gas filling the low-pressure chamber 7 passes through a low-pressure outlet 17 provided in the valve seat 3. It is supplied to the low pressure inlet of the compressor 9. Thus, a heating cycle is formed.

As shown in FIG. 2, when the switching rotor 4 rotates in the other direction by a predetermined angle about the rotation axis z, the second rotation is performed.
The high-pressure outlet 16 and the second heat exchanger connection port 13 communicate with each other, and the high-pressure refrigerant gas filling the high-pressure chamber 8 passes through the second high-pressure outlet 16 and the second heat exchanger connection port 13 to the other ends of the heat exchanger 11. Supplied to the end.

The rotation of the switching rotor 4 causes the first high-pressure outlet 15 to slide and rotate on the valve seat surface to open the first heat exchanger connection port 12 and to be led out from one end of the heat exchanger 11. The low-pressure refrigerant gas to be introduced is introduced into the low-pressure chamber 7 through the opened first heat exchanger connection port 12, and the low-pressure refrigerant gas filling the low-pressure chamber 7 is supplied to the compressor through a low-pressure outlet 17 provided in the valve seat 3. 9 low pressure inlet. Thus, a cooling cycle is formed.

[0027] Between the compressor connection port 10 and the high pressure inlet port 14, between the first high pressure outlet port 15 and the first heat exchanger connection port 12, and between the second high pressure outlet port 16 and the second heat exchanger connection port 1.
In order to achieve airtight communication between the three, first, second, and third sealants 18, 19 and 20 are provided.

As shown in FIG. 3, the first sealing material 18
Has a high-pressure inlet 14 with a cylindrical port 14 ', a compressor connection port 10 with a cylindrical shape, a nested structure with both cylindrical ports facing each other, and a ring-shaped sealing interposed between the peripheral surfaces of both cylindrical ports. In addition to airtightness, the switching rotor 4 is guided by the cylindrical port 14 'while maintaining the nested state of the two cylindrical ports.
Can be moved in the axial direction.

The second and third sealing members 19 and 20 use cylindrical sealing, and the first and second high-pressure outlets 15 and 16 are used.
Is opened on the side facing the valve seat 3, and the sealing materials 19 and 20 are inserted into the inner peripheral surface of the opening, and the inner end surface thereof is closely abutted against the annular step portion 21 at the bottom of the opening. The outer end surfaces of the members 19 and 20 are brought into close contact with the inner surface of the valve seat 3.

The second and third sealing members 19 and 20 are integrally attached to the inner peripheral surface of the opening with an adhesive or the like, or are movably tightly fitted along the inner peripheral surface of the opening. That is, the second and third sealing members 19 and 20 are movably held on the valve seat 3 in the crimping direction and the opposite direction, that is, in the direction of the rotation axis z.

As shown in FIGS. 3 and 6, an effective pressure receiving area S1 of the high-pressure inlet 14 for the high-pressure refrigerant gas and a total effective pressure-receiving area S2 of the first and second high-pressure outlets 15 and 16 for the high-pressure refrigerant gas. Are set in a relationship of S2 <S1. The pressure difference between the effective pressure receiving areas S2 and S1 causes a pressure difference to be applied to the switching rotor 4, and the switching pressure causes the switching rotor 4 to connect the first and second heat exchanger connection ports 12,
13, the switching rotor 4 is slightly moved in the same direction by this pressing force, and is interposed between the first and second high-pressure outlets 15 and 16 and the first and second heat exchanger connection ports 12 and 13. The second and third sealing materials 19 and 20 are connected to the high-pressure outlets 15 and 1.
6 and / or by press-fitting to the periphery of the heat exchanger connection ports 12 and 13 to form an airtight state. That is, the second and third sealing materials 1
9 and 20 are connected to the first and second heat exchanger connection ports 12 and 1.
3 is pressed against the surface of the valve seat 3 at the peripheral edge of the valve seat 3 so that the valve seat 3 is in close contact.

As described above, the second and third sealing members 19 and 20 are connected to the first and second high-pressure outlets 1 of the switching rotor 4.
5, 16 and the first and second heat exchanger connection ports 12 and 13,
When the switching members 4 are minutely moved in the direction of the rotation axis z due to the differential pressure, when the switching rotor 4 is minutely moved in the crimping direction and the opposite direction under the non-crimping direction, The end face is crimped to the annular step portion 21 and the outer end face is crimped to the inner surface of the valve seat 3.

As shown in FIG. 5, as an embodiment of the present invention, a supplementary pressure spring 22 for elastically pressing the switching rotor 4 toward the first and second heat exchanger connection ports 12 and 13 is provided. be able to.

The supplementary pressure spring 22 is interposed, for example, between the wall of the cup-shaped cover 2 where the compressor connection port 10 is provided and the wall of the switching rotor 4 where the high-pressure inlet 15 is provided. Then, the switching rotor 4 is elastically pressed toward the first and second heat exchanger connection ports 12 and 13. The position of the pressure-supplying spring 22 is not restricted to the position as long as the rotor 4 can be provided with the above-described elastic force.

The supplementary pressure spring 22 supplements the above-mentioned differential pressure effect, and as such, includes the second and third sealing members 19,
The one having a smaller spring constant is not used to ensure the close contact of 20.

The rotating shaft 23 of the switching rotor 4 penetrates through the housing 1, that is, the valve seat 3 of the housing 1, and protrudes to the outside, and is mounted on the inner peripheral edge of the through hole 24 so as to surround the rotating shaft 23. The switching rotor 4 is pressed against the fourth sealing material 25 by the differential pressure of the applied pressure, and the through hole 24 of the rotating shaft 23 is air-tight. Alternatively, the fourth sealing material 25 is integrally attached to the surface of the switching rotor 4 facing the valve seat 3 so as to surround the rotating shaft 23, or, similarly to the second and third sealing materials 19 and 20, the axis z. Hold it movably in the direction. Switching rotor 4 by the above differential pressure
Presses the outer end surface of the sealing material 25 against the surface of the valve seat 3 at the periphery of the through hole 24 as the micro-movement moves.

The rotating shaft 23 is connected to the valve seat 6 of the switching rotor 4.
, Is extended on the rotation axis z and protrudes outward from the valve seat 3, is rotated at a fixed angle by a drive source such as a solenoid or a motor, and causes the switching rotor 4 to reciprocately rotate.
Therefore, the rotation shaft 23, the compressor connection port 10, and the high-pressure introduction port 14 are arranged concentrically with each other about the rotation axis z.

As can be understood from the above description, the high-pressure inlet 14 is disposed at one end of the rotation axis z of the switching rotor 4, and the first and second high-pressure outlets 15 and 16 are disposed at the other end. Distribute.

Similarly, the compressor connection port 10 is provided at one end of the housing 1 on the rotation axis z, and the first and second heat exchanger connection ports 12 and 13 are provided at the other end.

In the switching device, the high pressure inlet 14
, Which is the projection surface of the high pressure inlet 14
Is a pressure receiving surface P. On the other hand, high pressure outlet 15,
The inner surface area of the cup-shaped cover 5 serving as the projection surface 16 is a pressure receiving surface P '.

As described above, the effective pressure receiving area S1 of the high-pressure inlet 14 for the high-pressure refrigerant gas and the total effective pressure-receiving area S2 of the first and second high-pressure outlets 15 and 16 for the high-pressure refrigerant gas satisfy S2 <S1. Although the relationship is set, the differential pressure due to this setting is applied to the pressure receiving surface P, and the switching rotor 4 is slightly moved toward the first and second heat exchanger connection ports 12 and 13, and the second and third heat exchangers are connected. , 4 sealing materials 19,20,
Obtain 25 crimps.

The pressure receiving surface P is arranged at the center of the switching rotor 4 on the rotation axis z and presses the rotor 4 in a well-balanced manner.

In the embodiment described above, one high-pressure inlet 14 is provided at one end of the switching rotor 4 in the direction of the rotation axis z, and two high-pressure outlets 15 and 16 are provided at the other end. In the embodiment described below, one high pressure inlet 14 is provided at one end of the switching rotor 4 in the direction of the rotation axis z as shown in FIGS. 7 and 8. One high-pressure outlet 15 is provided on the other end side to selectively switch between the first and second heat exchanger connection ports 12 and 13.

Speaking of the relationship with the above-described embodiment, the other structural principle is exactly the same as that of the above-described embodiment except that the second high-pressure outlet 16 is not provided.

That is, the switching rotor 4 has a high-pressure inlet 14 centered on the rotation axis z, and has a high-pressure outlet 15 at a position separated from the rotation axis z by a predetermined dimension. The high-pressure outlet 15 is connected to the first heat exchanger connection port 12 by rotating the same in one direction, and the high-pressure outlet 15 is connected to the second heat exchanger connection port by rotating the same in the other direction. 13 to form the cooling cycle or the heating cycle.

As described above, as shown in FIGS. 7 and 8, the effective pressure receiving area S1 of the high pressure inlet 14 for the high pressure refrigerant gas and the effective pressure receiving area S2 of the high pressure outlet 15 for the high pressure refrigerant gas are represented by S2 < Set to the relationship of S1.

The pressure difference between the effective pressure receiving areas S2 and S1 causes a pressure difference between the pressure applied to the switching rotor 4 and the switching pressure of the switching rotor 4 toward the first and second heat exchanger connection ports 12 and 13. The switching rotor 4 is slightly moved in the same direction by this pressing force, and the second sealing material 19 interposed between the high-pressure outlet 15 and the first and second heat exchanger connection ports 12 and 13 is moved to the high-pressure outlet. 15 and / or heat exchanger connection port 1
It is press-bonded to the peripheral edges of 2 and 13 to form an airtight state. That is, the second
The outer end surface of the sealing material 19 is pressed against the surface of the valve seat 3 at the peripheral edges of the first and second heat exchanger connection ports 12 and 13 so as to be brought into close contact therewith.

As described above, the second sealing material 19 is applied between the high-pressure outlet 15 of the switching rotor 4 and the first and second heat exchanger connection ports 12 and 13 in a crimping direction and a direction opposite to the crimping direction (not crimping). When the switching member 4 is minutely moved in the direction of the rotation axis z due to the above-mentioned differential pressure, the inner end surface of the sealing member 19 is annularly stepped. And the outer end face is pressed against the inner surface of the valve seat 3.

As described above, as an embodiment of the present invention, it is possible to provide a supplementary pressure spring 22 for elastically pressing the switching rotor 4 toward the first and second heat exchanger connection ports 12 and 13 as described above. It is.

As described above, the sealing member 25 for sealing the through hole 24 of the rotating shaft 23 can be press-bonded by the differential pressure.

The general formula of the differential pressure generated by the effective pressure receiving areas S1 and S2 is expressed by Formula 1 in the examples of FIGS.

[0052]

(Equation 1) Equations 2 are used in the examples shown in FIGS.

[0053]

(Equation 2)In Equations 1 and 2, P1 = high pressure (kg / cm^Two ) P2 = low pressure (kg / cm^Two ) ΦD = large diameter (cm^Two) (High pressure inlet side) φd = small diameter (cm^Two) (High-pressure outlet side).

As a specific example, in equations 1 and 2, P1 = 15 kg / cm^Two  P2 = 5kg / cm^Two  In the case where φD = φ18 φd = φ9.5, Equation 3 is used in the former case.

[0055]

(Equation 3) In the latter case, Equation 4 is used.

[0056]

(Equation 4)

[0057]

As described above, according to the present invention, the sealing material is pressed and moved while the switching rotor is pressed by the differential pressure without providing any special device or mechanism for pressing the switching rotor against the valve seat. By press-fitting, the airtight state between the high-pressure outlet and the heat exchanger connection can be reliably ensured, and the structure can be simplified to provide a highly reliable rotary type flow switching device.

[Brief description of the drawings]

FIG. 1A is a cross-sectional view illustrating the flow of high-pressure gas at the time of heating switching of a refrigerant gas flow switching device in a cooling and heating device according to an embodiment of the present invention, and FIG.

FIG. 2A is a cross-sectional view illustrating the flow of high-pressure gas at the time of cooling switching of a refrigerant gas flow switching device in a cooling and heating device according to an embodiment of the present invention, and FIG.

FIG. 3 is a longitudinal sectional view showing a specific structure of the switching device, in which a switching rotor can be longitudinally cut.

FIG. 4 is a transverse cross-sectional view of the switching rotor.

FIG. 5 is a longitudinal sectional view of the above-described device showing an example in which a supplementary pressure spring is provided.

FIG. 6 is a plan view illustrating an effective pressure receiving area of a high-pressure inlet and a high-pressure outlet in the switching device.

FIG. 7 is a longitudinal sectional view showing another example of the switching device.

8 is a plan view illustrating effective pressure receiving areas of a high-pressure inlet and a high-pressure outlet in the switching device in FIG. 7;

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 1 Housing 3 Valve seat 4 Switching rotor 6 Valve seat 7 Low-pressure chamber 8 High-pressure chamber 9 Compressor 11 Heat exchanger 12 First heat exchanger connection port 13 Second heat exchanger connection port 14 High pressure inlet 15 First high pressure outlet 16 Second high-pressure outlet 18 First sealing material 19 Second sealing material 20 Third sealing material 22 Supplementary pressure spring 23 Rotating shaft 25 Fourth sealing material P Pressure receiving surface P 'Pressure receiving surface S1 Effective against high pressure refrigerant gas at high pressure inlet Pressure receiving area S2 Effective pressure receiving area for high-pressure refrigerant gas at high-pressure outlet port z Rotation axis

Claims (4)

(57) [Claims] 1. A switching rotor is built in a housing, and the housing has a compressor connection port connected to a high-pressure outlet of a compressor and two heat exchanger connection ports connected to one end and the other end of the heat exchanger. On the other hand, the switching rotor has a high-pressure inlet communicating with a compressor connection port, and a high-pressure outlet selectively communicating with any one of the heat exchanger connection ports. In the cooling gas passage switching device in the cooling and heating device configured to achieve the selective communication by rotating in the direction, an effective pressure receiving area S1 for the high-pressure refrigerant gas at the high-pressure inlet and the high-pressure refrigerant gas at the high-pressure outlet are provided. And the effective pressure receiving area S2 with respect to the pressure is set in a relationship of S2 <S1, and the switching rotor is minutely moved in the direction of the heat exchanger connection port by the differential pressure of the applied pressure based on the pressure receiving area difference between S2 and S1. A sealing material interposed between the high-pressure outlet and the heat exchanger connection port is pressed against the periphery of the high-pressure outlet and / or the heat exchanger connection port to form an airtight state. Channel switching device. 2. The method according to claim 1, wherein the sealing material is disposed between the high-pressure gas outlet of the switching rotor and the heat exchanger connection port so as to be able to move slightly in the crimping direction and in the opposite direction under non-crimping. Item 2. A refrigerant gas flow switching device in the cooling and heating device according to Item 1. 3. A refrigerant gas flow switching device in a cooling and heating device according to claim 1, further comprising a pressurizing spring for elastically pressing said switching rotor toward a heat exchanger connection port. 4. The rotating shaft of the switching rotor is projected outside through the housing, and the rotor is pressed against the sealing material disposed on the inner peripheral edge of the through-hole by the pressure difference of the applied pressure. 2. A flow path switching device for a refrigerant gas in a cooling and heating device according to claim 1, wherein the airtightness of the refrigerant gas is maintained.